Apparatus for milling complex surfaces



1953 c. B. DE VLIEG 2,660,931

APPARATUS FOR MILLING COMPLEX SURFACES Filed Sept. 19, 1947 12 Sheets-Sheet l INVEN TOR.

CHARLES 5. DE V/JEG Dec. 1, 1953 Filed Sept. 19, 1947 C. B. DE VLIEG APPARATUS FOR MILLING COMPLEX SURFACES 12 Sheets-Sheet 2 INVENTOR. CHARLES B. D: Muss ATT Dec. 1, 1953 Filed Sept. 19, 1947 C. B. DE VLIEG APPARATUS FOR MILLING COMPLEX SURFACES 12 Sheets-Sheet 3 INVENTOR. CHARLES 15. DE VL/EG ATTYS.

Dec. 1953 c. B. DE VLIEG 2,660,931

APPARATUS FOR MILLING COMPLEX SURFACES Filed Sept. 19, 1947 12 Sheets-Sheet 4 INVENTOR. CHARLE S 5. D5 VLIEG ATTYS.

I c. B. DE VLIEG APPARATUS FOR MILLING COMPLEX SURFACES Dec. 1, 1953 12 Sheets-Sheet 5 Filed Sept. 19, 1947 wow {Q N INVENTOR- CHARLES 5. D5 l/use C. B. DE VLlEG APPARATUS F OR MILLING COMPLEX SURFACES Dec. 1, 1953 12 Sheets-Sheet 6 Fil ed Sept. 19. 1947 INVENTQR CHARLES B. D: VLIEG Dec. 1, 1953 c. B. DE VLIEG APPARATUS FOR MILLING COMPLEX SURFACES l2 Sheets-Sheet 7 Filed Sept. 19, 1947 INVENTOR. v CHAR/.55 B 015 Vuss BY f $2 -m NM 7/// 7/% vm mN wmw wmN MU mN o at E: v Pm um 23 Dec. 1, 1953 C. B. DE VLIEG APPARATUS FOR MILLING COMPLEX SURFACES Filed Sept. 19, 1947 CHARLE 5. D5 Vuzc Mww 12 Sheets-Sheet 8 INVENTOR.

ATTYS.

Dec. 1, 1953 c. B. DE VLIEG APPARATUS FOR MILLING COMPLEX SURFACES Filed Sept. 19, 1947 12 Sheets-Sheet 9 INVENTOR.

CHARLES B. 0.6 Vuss ATTYS.

A D c. 1, 1953 c. B. DE VLIEG 2,660,931

APPARATUS FOR MILLING COMPLEX SURFACES Filed Sept. 19, 194'? A 12 Sheets-Sheet 10 e v 0 q- 8; 1a 3 *6 & Q

INVENTQR. CHAR/.58 B. 05 Vuzs Dec. 1, 1953 c. B. DE VLIEG APPARATUS FOR MILLING COMPLEX SURFACES INVENTOR. CHARLES B. D: Vuzs Dec. 1, 1953 c. B. DE VLIEG APPARATUS FOR MILLING COMPLEX SURFACES 12 Sheets-Sheet 12 Filed Sept. 19, 1947 llll] HITI MIMI i \w G L M INVENTOR. CHARLES 8. 0E VL/fG ifzz/M AT TYS.

Patented Dec, 1, 1953 APPARATUS FOR MILLING COMPLEX SURFACES Charles B. De Vlieg, Farmington, Mich., assignor to Thompson Products, Inc., Cleveland, Ohio, a

corporation of Ohio Application September 19, 1947, Serial No. 775,109

5 Claims.

This invention relates to a machine tool for generating a complex surface on a workpiece by cutting, milling, grinding, or similar material rcmoving operations, and particularly, to a machine for milling in a single operation by a single cutter the complex surface of a blade or vane of an impeller wheel of the type employed in aircraft compressors or turbines.

As to certain features, this application con stitutes a continuation in part of the pending application of Charles B. De Vlieg, Serial No. 564,107, filed November 18, 1944, and not Patent No. 2,480,807, granted August 30, 1949, and

the pending application of Charles B. De Vlieg, Serial No. 748,282, filed May 15, 1947.

The recent wide-spread adoption of jet type engines for aircraft has resulted in an unprecedented demand for machine tools capable of producing the complex generated surfaces required for the blades of the impeller units, compressors and the turbines employed in conjunction with such jet engines. It happens that the type of blade surface which will yield optimum adiabatic operating efficiency is of extremely complex configuration in that no section of the blade taken along the length axis of the blade will be identical to any other section, and furthermore, the various successive sections along the length axis of the blade may be angularly displaced with respect to each other. However, such blade surfaces do include one property which permits them to be fabricated upon a machine tool in a single operation by a single cutter and that is the fact that each blade surface, or discrete portions of each blade surface, may be considered to be generated by a line moving in a complex path involving both linear and rotational displacement of the generating line. Of course, in those blade corigurations wherein only a portion of the blade surface is generated by such a moving line, it will be understood that a separate machining operation is necessarily performed for each separately generated surface portion of the blade.

In the first of the above referred to copending applications, there is disclosed and claimed a machine tool construction and a metal working method by which vane surfaces of relatively simple configuration may be generated by the relative movements of a rotating cutter and a workiece, such relative movements, of course, being produced by such machine. Briefly, the method and apparatus disclosed in the first of the above referred to copending applications contemplates a total of not more than three relative movements of the rotating cutter and the workpiece upon which a vane surface is to be generated. The first of such movements constitutes a relative rotation of the workpiece with respect to the rotating cutter about a selected axis. The second movement embodies a relative linear displacement of the rotating cutter and workpiece along such selected axis, and the third move ment embodies a lateral relative displacement of the rotating cutter and workpiece in a direction substantially perpendicular to the selected axis.

' The second of the above referred to copending applications discloses and claims methods and apparatus for generating a much more complicated vane surface upon a workpiece by the metal removing action of a single rotating tool, such as a milling cutter. In addition to the three relative movements embodied in the machine construction of the first of the copending applications, the methods and apparatus of the second copending application utilizes two additional relative movements of the rotating cutter with respect to the workpiece. Such additional movements, which may be applied concurrently or individually to the three relative movements heretofore indentified, constitute a relative linear advancement of the rotating cutter with respect to the workpiece in a direction along the axis of rotation of the rotating cutter, while the last relative movement constitutes a pivotal shifting of the rotating cutter about an axis which is transverse to the axis of rotation of the cutter. It will be recognized by those skilled in this art that the five relative movements which are available between the rotating cutter and the workpiece in the methods and apparatus disclosed in the second of the above referred to copending applications will permit the generation of any vane surface upon a workpiece irrespective of the complexity of configuration of such vane surface, provided only that discrete portions of the vane surface are shaped so as to be capable of generation by a line moving along a complex path.

The apparatus of this invention constitute an intermediate development both chronologically and structurally between the methods and apparatus respectively disclosed in the above referred to copending applications. Thus, this invention contemplates the generation of a complex surface upon a workpiece by the material removing action of a rotating tool wherein a total of four relative movement components may be concurrently produced between the rotating tool and the workpiece. Such relative movement components respectively comprise a rotation of the workpiece about a selected axis which is preferably substantially perpendicular to the axis of the rotating cutter. Concurrently, the workpiece and the rotating cutter may be linearly displaced by a component movement in the direction along the axis of rotation of the workpiece. Thirdly, the rotating cutter and workpiece may be linearly displaced by a movement component in a direction substantially perpendicular to the axis of rotation of the workpiece. Lastly, the rotating cutter and the workpiece may be linearly displaced by a movement component in a direction along, the axis of the rotating cutter. Such combination of four relative movement components permits the generation of a vane surface upon 'aworkpiece of any complex surface configuration wherein; discrete portions of the vane surface are generated by a line moving along a complex path, limited only to those types of generated surfaces wherein the moving line remains substantially parallel to itself along all positions of its surface generating path.

It is therefore apparent that the apparatus of this invention provide for all of the relative movements of the workpiece and rotating cutter which may be produced by the methods and apparatus of the second of the above referred to copending applications, except for the relative movement embodying a pivotal shifting of the rotating cutter about an axis transverse to its axis of rotation.

A machine embodying this invention may be conveniently employed to generate a vane surface upon a single vane element'or, if desired, to generate successive circumferentially displaced vane surfaces upon an impeller blank workpiece.

Accordingly, it is an object of this invention to provide an improved apparatus for generating 'a complex surface upon a workpiece by asingle operation of a single materialremoving tool.

A particular object of this invention is to provide an improved apparatus for milling in a single operation with a'single cutter, the complexsurfaces employed on the vane of impeller wheels or similar articles. 7

A further object of the invention. is to provide a metal working machine capable of machining in a single operation an irregular generated surface on an article of manufacture in which the contour of any cross section varies from side to side or end to end, respectively.

Still another object of the invention is to provide a metal working machine capable of producing a plurality of coordinated relative motions between a rotating metal removing tool and a workpiece in which all motion producing. elements of the machine pass through cycles of forward and reverse direction of movement without backlash, whereby generated surfaceson articles of thin cross section can be positively and-accurately machined.

A still further object of the invention isto provide a metal working machine capable of producing a complex generated surface upon a work'- piece within limits of precision tolerances and by a single, rapid metal working operation, permitting the fabrication of such complex surfaces in larger quantities and at less cost than the machines or methods heretofore known have permitted.

A particular object of the invention is to provide an improved apparatus for machining an air foil surface on an impeller blade of the type used in aircraft superchargers, turbines and jet propulsion engines.

The specific nature of the invention, as well as other objects and advantages thereof will become apparent to those skilled in the art from the following detailed description of the annexed sheets of drawings which, by way of preferred example only, illustrate two specific embodiments of the invention.

On the drawings:

s Figure 1 is a front elevational view of an assembled machine embodying this invention;

Figure 2 is-a-sicle elevational view of an assembled machine embodying this invention;

Figure '3 is a top plan view of an assembled machine embodying this invention; Figure 4 is aschematic perspective view of the machine of Figure 1, with parts omitted for clarity, showing all of the moving elements of the machine employed forv producing the various coordinated relative movements of the rotating cutter and the workpiece;

Figure 5' is an enlarged scale, partial top plan view, with parts thereof in section on line V-V of Figure 2, of a portion of themachine of Figures 1 through 3;

Figure 6 is an enlarged. scale, partial sectional view taken on the plane VI-VI of Figure 8;

Figure 7 is an enlarged. scale, partial sectional view taken on the plan'eVII-VII of Figure 3;

Figure 8 is a sectional view taken on the plane VIIL-VIII' of Figure 7 ;v

Figure 9 is an 'enlargedscale, partial sectional view taken on the plane lX-IX of-FigureB;

Figure 10 is an enlarged scale, partial. top plan view of a portion of the machine of Figures 1 through 3;

Figure 11 is asectional view taken on the plane Xi-XI of Figure 10;

Figure 12 isv a partial sectional view taken on the plane XII-a-XII of Figure 10;

Figure 13 is a top plan view. of a portion of the bed of the machine showing the cooperation of the trip dogs with the motor controlling switches; V Figure 14 is a partial sectional view taken on the plane XIV.-XIV of Figure '13;

Figure I5 is aside elevational view of that portion of the apparatus shown in Figure 13;

Figure 16- is afipartialsectional View, taken on a plane passing through the axis of the workpiece supporting spindle, of the indexing mechanism;

Figure -17 is a partial end elevational view, partly in section, of the workpiece indexing mech anism;

Figure 18 is a schematic electrical circuit diagram-illustrating the control circuit employed for the various motors of the machine;

Figure 1-9 is a schematic fluidcircuit diagram illustrating the fluid connection for the various hydraulic devices of the machine; and

Figure 20 is a partial elevational view illustrating a modification of this invention wherein an individual vane element workpiece is operated onby the machine.

As shown on the drawings:

Referring particularly to Figures 1 through 3, a machine embodying this invention may comprise an elongated bed frame If! upon one end of which is rigidly mounted in any suitable manner an upstanding pedestal H. A carriage i2 is mounted on bed frame 5 3, in a manner to be described in more detail later, for movement lengthwise of the bed toward and away from the pedestal ii. A spindle i3 is suitably journaled in carriage [2 for rotation about an axis which is generally parallel to the direction of movement of the carriage l2.

A second carriage M is mounted on the pedestal I l, in a manner to be described in more detail later, for movement generally transversely of such pedestal, i. e., in a direction substantially perpendicular to the direction of movement of the first carriage i2. A sub-carriage i is then movably mounted on the second carriage M for movement in a vertical plane, which movement is substantially perpendicular to both of the directions of movement of the first and second carriages i2 and M, respectively. A spindle i6 is suitably journaled in sub-carriage 5 for rotation about a vertical axis, which will be recognized to be an axis which is substantially parallel to the direction of movement of the sub-carriage 15.

It is therefore apparent that a variety of components of relative movement may be produced between the spindles l3 and I5 depending upon the rotative movements imparted to such spindles and the linear movements imparted to the first carriage l2, the second carriage l4 and the sub-carriage l5. Those skilled in the art will also recognize that in any material-removing operation, such as milling, it is immaterial whether the workpiece or the rotating tool is actually moved, so long as the necessary components of relative movement between the workpiece and rotating tool are produced. Therefore, either the spindle I 3 or the spindle It could be employed to mount either the workpiece or the rotating tool and identical relative movements of the workpiece and rotating tool could be obtained in either case by obvious modifications of the machine.

In the particular example illustrated in the drawings, the spindle I3 is employed to mount a workpiece W, which, in the modification illustrated in Figures 1 through 1'7 is shown as coinprising an impeller wheel blank of the integral vane type, while in the modification illustrated in Figure 2f), the workpiece W may comprise an individual vane element of a non-integral impeller assembly. In both modifications, the rotatable spindle I6 is employed to mount the rotating tool T which is shown as comprising a side cutting, milling cutter, but may obviously comprise any other form of rotatable, materialremoving tool including a grinding element.

When an integral impeller blank workpiece W is to be operated on, it is, of course, necessary to provide some form of indexing mechanism which will eifect the successive positioning of the workpiece blank W in a plurality of angularly separated positions with respect to the rotating tool T, so that such tool may successively generate a plurality of circumferentially separa ed vane surfaces on the workpiece blank. The details or" the particular indexing mechanism employed will be described later.

Referring now to Figure l, the relative movements between the workpiece W and the rotating tool T and the means for accomplishing such relative movement will be described in a general manner so that the later description of the details of the machine construction may be more clearly understood. It should be clearly understood, however, that the relative movements effected between the rotating tool T and the workpiece W constitute a particular merit of this invention, and while the mechanism illustrated for producing such relative movements reprecents a preferred mechanical arrangement, a

6 variety of equivalent arrangements will readily suggest themselves to those skilled in the art.

Thus a motor 2c is provided which, through pulley 29a, belt 20b, pulley 2510, worm 2M, and worm gear 26c drives a splined shaft 2i to which the worm gear 253:; is keyed. Splined shaft 2! in turn drives through idler gears Zia, fill), 250, idler shaft Zld, pinion 21c and gear 22s, a lead screw 22, which is threadably engaged with a first carriage 12 so that rotation of lead screw 22 produces a lineal movement of carriage i2 along the bed frame it. There is thus produced between the workpiece W and the rotating tool I a first relative movement constituting a linear displacement in a direction substantially parallel to the axis of rotation of the workpiece W, hence producing a relative movement component along the axis of rotation of the workpiece W.

The workpiece W is concurrently rotated about the axis of spindle is in timed relationship to the lineal movement of carriage #2, by a cam and follower mechanism comprising a contour cam B which is relatively longitudinally movable with respect to the carriage l2 and thereby produces transverse displacement of a cam follower unit 23 which has a roller 23c journaled in one end thereof and engaged with the contour of cam B. The other end of cam follower unit 23 is provided with rack teeth 2% which are engageable with a large gear 2-? which is connected to the spindle l3 so as to produce a rotation of such spindle and hence of the workpiece W as a function of the contour of cam B. To eliminate any effects of backlash in this mechanism, a biasing force is applied to the cam and cam follower mechanism by a hydraulic unit 25 which has the piston portion 25a thereof secured to a cylindrical rack member 2% which is meshed with a gear 27 also secured to spindle l3. A constant pressure is thereby applied through cylinder unit 25 to maintain at all times tight engagement between gear 2 and rack portion 23b of cam follower 23 as well as to maintain the cam follower 23 in snug engagement with the cam surface of cam B.

It is obvious that the cam B may, if desired, be rigidly mounted on the bedframe it and the rotational movement of the workpiece W, about the axis of spindle it derived from cam B and cam follower 23 by the lineal movement of the carriage 12 along the bedframe It. However, it often happens that the extent or required lineal movement of the carriage H? for a particular workpiece W is quite limited, so that to produce the required amount of rotational movement of the workpiece W about the axis of spindle it would require that the cam B have a very steep contour. To improve this condition, the cam B may also be linearly moved with respect to bedframe It] to permit a reduction in the steepness of the contour of cam 3. Such lineal movement may be conveniently derived by permitting the splined shaft '2! to move with the carriage i2 and providing a threaded portion 2! on the end thereof to engage with a threaded bracket portion 2m to which cam B is secured so that the rotation of splined shaft 25 produces the desired relative displacement of cam B with respect to cam follower unit 23.

There has now been described the mechanism for producing two coordinated compon nts of relative movement between the workpiece W and the rotating tool T comprising respectively, a rotation of the workpiece W about a selected axis and a relative lineal displacement of the workpiece W with respect to the tool '1" in the direction of such selected axis. The two additional coordinated components of relative movement may be derived by shifting the position of the spindle it which carries the rotating tool '1. For this purpose, gears 219' and 2110 provide a power tal e-off from splined shaft 25 to drive a shaft 23 extending along the bed frame to to a point within the pedestal portion H wherein a worm 28a drives a transversely extending shaft 2 9 through worm gears 5a.

A contour C is sl'idably mounted in the pedestal portion 5 i for lengthwise movement. The cam C is linearly shifted with respect-to pedestal portion 5 l in timed relationship to the previously described lineal movements]? the workpiece W by a pinion on shafit' which engages a rack to secured in relationship to cam *0.

Second carriage i' which will'be remembered as being mounted for transverse movements with respect to pedestal portion i i, has a cam follower unit 3i rigidly secured thereto and having a roller tic journaled in its projecting end which cooperates with tr e cam surface of cam C. Hence the movement of cam C results in a lateral displacement of second carriage i l and hence in a third componentoi relative movement between the workpiece W and the rotating tool T which constitutes a lineal displacement in a direction substantially perpendicular to the axis of rotation ofthe workpiece W.

To eliminate backlash in this portion of mechanism, the en ire second carriage i-d-is'urged toward the care. C by a pressure cylinder unit 32, the cylinder portion 32a of which is fixedly mounted on the pedestal ll and the piston portion 3% is rigidly secured to second carriage 'l' i. Suitable hydraulic or pneumatic pressure applied to cylinder unit 32 to maintain a force on second carriage i i urging the cam follower unit 31 into snug engagement with the cam surface of cam C.

To provide the fourth component of 'coordi nated relative movements of the workpiece W and the rotating tool the end of shaft 29 is splined, as indicated 28b, and a pinion 2190 is secured to such spl ined' portion. Einion 2E0 drives a gear 23c through an idler 2%, and gear 29c cooperates with a rack 3i which is secured in depending relationship to a contour care A. The cam A is mounts.t in the second carriage i i ior movement a direction generally parallel with the length of the bed frame it. The subcarriage which, it will 'be'recallcd, is movably mounted on the second carriage is for generally vertical mcwements, is provided with a cam follower bracket 33 having a roller 3% in a projec'ting end thereof which engages the cam contour of cam A.

Thus a third and fourth component or relative movement between theworkpiece /V'and the rotating tool '1 are produced which are respectively controlled by the cams A; and .C. The cam C controls the component of relative movement in a direction substantially perpendicular to the sunset rotation of the workpieceW while the cam A controls the component of relative movementv in a direction aligned with the aXis of the spindle is which carries the rotating tool I.

In order to effect rotation of they tool T,,a driving motor 3% is mounted on thesecondcarriage i l and is directly connected through a belt drive and a plurality of gears to .a gear .357 which secured to a splined portion 5.80:, of the spindle as. Home the cutting tool '1 .is rotated independently of the. vertical movements of spindle i-Bproducedby displacements of the sub-carriage i5 controlled by cam A.

It will be obvious to those skilled in the art that the-aforedescribcd four relative movements between the workpiece W and rotating tool T will permit the rotating tool T to generate a complex vane surface on the workpiece W. The characteristics of the generated vane surface will, of course, depend upon the particular contour oi the cams A, B and C and the selected relationships of the movement or" such cams with respect to each other and to the axial movement of the workpiece W produced by the lead screw 22. Ohviously, a plurality of such vane surfaces may be generated on the workpiece W by successively angularly indexing the workpiece W with respect to the ax-is of spindle l3; Generally, only one face of each vane-o1" the finished impeller will be machined on one machine, inasmuch as the opposite face usually has d'nerent shape characteristics ofits generated surface and as a matter of manufacturing economy, it is much more practical to utilize a second machine for generating the opposite face of the vane rather than resetting the cams of one machine. However, it should be understood that any one machine constructed in accordance may be utilized to generate either i ace of a vane.

lit-should be further noted that the relative movement component along the axis of the rotating tool i may be eliminated without affecting the vane-generating characteristics oi the remaining three relative movements. Such axial relative movement or" the rotating tool T is employed to generate a desired hub contour for the vane,'and 1 511113113 impeller designs, the hub contour is relatively simple, involving a surface which is generally cylindrical with res' ect to the axis of the workpiece W. In such cases, the relative axial movement of the rotating tool T may be eliminated simply by providing a cam A having a uniform cam-contour and thus maintaining the rotating tool Tin the-same axial position throughout the milling operation.

With the general function and operation of the machine now in mind, the following detailed description of the elements of the machine wi be more readily understandable. Referring to Figures 5 and 6, it will ice-observed that the first carriage i2 is provided on its underside with a generally dovetailed groove ll and longitudinal rib 12 which respectively engage correspondingly shaped ways it and dd provided on bed frame It in longitudinally extending arrangement thereon. A jib (l5 overlies the rib and is bolted to bed frame It to secure the carriage E2 to bed frame It for-sliding movements thereon.

A gear box '46 is mounted on the end of bed frame H] opposite the pedestal l i and the various gears and shafts 2i, i'i'a, Bib, tic, Zlcl, Elie, 22a and 22 are journaled in the gear box d8 in conventional fashion. The driving motor 2% may be conveniently mounted on the top of gear box t5 and the belt connection 2% to the splined shaft 2'! will beenclosed within a belt housing 26;.

As previously indicated, the splined shaft 2! is secured to the movable first/carriage it for linear movement therewith. Such securement is effected by a bearing bracket il (Figure 5) integrally formed on the side of movable carriage l2 and receiving a conventional anti-friction unit 410. whichv rotatably journals splined shaft 2i and inadolition, secures the shaft 2 l to the bracket 41 against any relative axial displacements.

Referring particularly to Figures 6, 7 and 8, it

will be observed that the work-supporting spindle I3 is journaled within an upstanding hollow housing 48 which is suitably bolted to the forward edge of the movable carriage [2. A longitudinally extending hollow bore 48a is defined by such housing, and an indexing sleeve element 49 is rotatably journaled therein by suitable anti-friction and thrust bearings 59a, 49b, 49c and 49d. Spindle I3 is rotatably journaled in the hollow bore of sleeve 49. Spindle i3 is provided at its front end, i. e., the end nearest spindle It, with an enlarged head portion respectively defining a first annular conical surface 53a and forwardly from said first surface a second annular conical surface 13b of larger diameter. Conical surface I3a is disposed adjacent a similarly shaped, but oppositely inclined, surface 492 provided on the front end of sleeve 49, and an adjustable clamping ring 59 is tightened about the conical'surfaces Ba and Md sufliciently to take up any backlash in the assemblage of spindle I3 and sleeve 49.

The larger annular conical flange portion [3b abuts a similarly shaped, but oppositely inclined flange portion m formed on a work holding fixture 5i, and an adjustable clamp 52 tightly surrounding the flanges ltb and 51a effects a rigid securement of work holding fixture 5| to the spindle I3.

Both the spindle l3 and the sleeve 49 project rearwardly out of their supporting housing 38 (Figure 16). In turn, the spindle l3 projects rearwardly beyond the extremity of sleeve 49 and an indexing hub member 53 is secured to the projecting end of spindle !3 as by a key 5342 and bolted end plate 53b. An annular indexing ring 54 is secured to the front face of indexing hub 53 as by suitable bolts 54a. Indexing ring 54, is provided with a plurality of circumferentially spaced, radial holes 5412, each of which is adapted to snugly receive the shank portion of an indexing pin 55. v

The rearwardly projecting portion of sleeve 49 has a hub 56 secured thereto as by a key 56a and this hub has an integral, axially projecting, flange portion 55b projecting from its rear face to snugly interfit within the bore of the indexing ring 54. At least one radial hole 560 is provided in axial flange portion 56b to snugly receive the end of the shank portion of the indexing pin 55.

It is therefore apparent that the angular position of the spindle It with respect to the sleeve 49 may be selectively adjusted by successively aligning the radial holes 552) of the indexing ring 54 with any single hole 560 of the hub member 56 and inserting the indexing pin 55 into the aligned holes. Thus the workpiece supporting fixture 5! may be selectively indexed throughout a plurality of angularly spacedpositions with respect to the spindle it. Obviously, the spacing between the successive indexing positions is selected to correspond to the desired location of the vanes upon the finished impeller wheel; I

The linear movement of the workpiece supporting fixture 5 i and hence of the workpiece W; along the axis of the spindle is is, of oourse;pro-

duced by the movement of the first carriage l2.- As previously indicated, the concurrent rotational: movement of the workpiece W about the axis ofthe spindle I3 is produced by the action of rack. portion 23b of the cam follower. unit 23 upon the gear 24 which surrounds and is keyed to the'sleeve s9. Cam B is secured to a horizontal ledge pro vided on a hollow interior-1y threaded block sowhich'isslidably mounted on bed frame is by channel We. The anti-backlash gear 2'! which urges the cam follower 23 against the cam surface of cam B may be conveniently formedintegrally with the gear 2t. Both the rack portion 23b of the cam follower 23 and the cylindrical rack 26 of the hydraulic anti-backlash cylinder 25 may be slidably journaled in suitable holes 51 (Figure 7) transversely disposed within the housing 48. Cylinder it may conveniently comprise a sleeve having a large flange portion 2572 which is bolted to. the side of housing 43 with the bore thereof in alignment with the hole 5'? which accommodates the anti-backlash rack 26. A suitable inlet pipe 250 may be provided in communication with oylinder 25, as well as a bleed pipe (not shown) to return fluid which has leaked past the piston to a suitable hydraulic reservoir.

To provide for initial adjustment of the relative angular position of the spindle 13 with respect to the rotating cutting tool T, a micrometer extension mechanism 69 is mounted in the cam follower unit 23 intermediate the rack portion 23b and the cam follower roller 23a. Micrometer mechanism Eill may comprise any one of several well known forms which is capable of minute adjustment to change the relative length of the cam follower mechanism and then to be rigidly clamped in any adjusted position. It is, of course, understood that such adjustment is made in the initial set-up of the machine for any particular vane generating operation.

Considering now the mechanism for driving and relatively shifting the rotating tool T, referonce is particularly made to'Figures 9 through 12 of the drawings. .As was previously indicated, the second carriage it is mounted on pedestal portion I i for generally transverse movement. Such mounting may be accomplished in conventional fashion, such as by providing cooperating ways on the underside of second carriage it and the top side of pedestal portion il; Such ways Ila and i lb may be partially seen in Figure 4.

The cam C which controls the transverse posi tion of the second carriage Id with respect to the pedestal-portion I! is mounted upon a horizontal ledge on aslide block El (Figure 9) which has the sides thereof slidably mounted in longitudinally extending grooves'defined between jib plates as and ways He formed on the pedestal H. The gear drive for shifting'cam C in a generally longitudinal direction with respect to the bed It has alreadybeen described in sufficient detail.

The cam follower mechanism 3! through which the cam C controls the transverse position of the second carriage it comprises a bracket member 53 which has a base plate portion @354 which is adjustably mountable upon a projecting plate Me which is suitably rigidly secured to the second carriage M. Plate Me is provided with .elongated slots Md which receivebolts Bdfor effect, ingthe adjustable securement of the bracket e3 thereto. In addition, a micrometer type positioning unit E5 is provided which operates between a rib. 63b onbracke't $3 and the movable second carriage M to permit a minute adjustment of the position of bracket 53.with respect to movable carriage is to be accomplished. As was previously indicated, backlash between cam C and the cam follower roller 3 la is eliminated by the biasforce exerted by a pressure cylinder unit 32. Cylinder unit 32 may be conveniently mounted on pedestal portion H, underlying the movable second carriage It. An angle bracket l-td is bolted to the side of movable carriage it and a dependan inlet conduit 32c and ing portion thereof ionsilec, 29d, and 23a ior efie'ctingithe driving 1 connectionxto'the camrA. Thepinion 2&0 which is secured to the splined'portion rofithe'shaft :25, isrota'tably jiournaled' vwithin; adepending bracket portion Mg provided ontl'removable second carriage is directly beneath the slot 147. wsiuitahle anti-friction hearing elements 29'! are provided for this :piniontsoiasitorsecure the "pinion to the second carriage ii 4 .for ;.linear movements but to freely permit I its :rotational :movement produced by the 'splined shaft 29 :and transmitted through intermediate gearsizild and .2512 to'the camrA.

.ThQC9-m;.A is mountedonralslide bio'ck G6 which isisli'dflbly mounted .LiIl ways 14h ii'ormed on the movable carriage l li-on eac'h sid'e of the vertical slot 1 d1. Removable jibe e1 zretaintthezslide block fidinassembly onthe ways nth. Theiraclreiement 3? for driving the camAis'secured'in depending relationship to' the'slide block EB,

As bestshown in riigures'e and 10, themovable second carriage M defines a pair of transversely spaced, vertically :extendingways 14k in which are received complementary shaped ways sea of a splndle'supporting'irame 68* "The relative vertical'movement between spindle supporting frame as and thesecond carriageHi is provided solely for the'purposes oi fadjustingthe initial verticalpositionror "the spindle IG, and hence the cutting .tool "T, with respect to the workpiece W. Aiter adjustment of such position by any suitable manually operable screw mechanism (not shown) the spindle supporting frame 68 is rigidly clamped'in position by'tightening oi adjustable 'jib 68b.

Onone side of the spindle "support *frame E8 there is defined apair 'ofspacedxvertically extending ways 59 which respectively receive correspondingly shaped projections '1 nwprovided on opposed edges of a'slideplatelc. Attire-bottom of slide plate W, the-cam follower mechanism "33 is mounted, providing contact'with the cam surface of cam A tocontrol'the vertical-positionof slide plate Hi. Slide plate 1o is'retained within the ways Eli by a pair of removable jibs 10b.

The cam follower mechanism '33 comprises a bracket having 'a plate portion 33a (Figure 1) nomically manufacturable machine structure for adjustably secured to slide plate :Tli through the cooperation of bolts 631) with elongated slots Hi0 in slide plate it. A micrometer position adjusting mechanism H isprovidedoperatinc'between camfollower 33 and an angle bracket 12 rigidly secure'd'to the top of'sli'deplate in. A minute'adjustment of the 'verticalposition of "slide plate Hi withrespect to the 'camisur'fa'ce or camie'rriay mechanismll and 6 locked in adjusted be effected by the micrometer then the assemblage rigidly position by tightening of the bolts 33?).

.Reierring p2 rticularly to Figure 12, .it will be seen that the slide plate'lil hasz an off-set bearing'bracket Hid rigidlysecuredthereto at its-top end by jibs Hie. I-he spindle 16 is rotatably' supported in bracket Hid by anti-friction bearing elements 161) and thus secured for :axial move ments Withithe slide plate Iii. Additionalilateral supportior spindle leis provided by ta driving i2 sleeve 15 :tconventionally 'journaled :in Ia :suitabLe recess did .in. spindlevsupp'ort :frame .iiB.

A'Irotating cutting tool .T, which is shown as comprising :a spiral, edge cuttin type, tapered milling cutteriis secured to the bottom end of spindle ltliywhichprojects out or the overhanging portion o1 spindle supportiframe es to-overlie the bed frame l0, and hence the cutting tool T may'bermovie'd into cooperative engagement with the "workpiece W.

fAs was previously mentioned, a motor as is provided for driving the spindle wi3 and such motor may "be conveniently imounted a ver ti'cal axis position on the side of the movable carriage It. Through a belt d and pulley '(Figurell), the motor drives a'vertical shaft 35 suitablyjourneledincarriage l4. .At 'an'intermediate portion on shaft 350, a gear the! is provided which drives a vertical splined shaft 35c through agear The bottom portion tip of vertical shaft iseccentrically formed and is utilize'clto *drive a reciprocating type pump Hi. The pump T4 maybe employed to provide hydraulic ipressure for the anti-backlash cylinders or for distributing coolant, as desired.

The top end of splined shaft 35c is suitably journaled in the carriage l4 while the bottom portion thereof projects into a vertical bore 33f provided in the spindle support frame 68 and is journaled-therein by suitable anti-friction bearings A gea'r sfih is keyed to the splined shaft are and through an idler gear drives a spindle sleeve gear 35?. The splihed shaft permits the vertical adjustment of the spindle supportirame 6'8 with respect to the vertically stationary portion of the movable second carriage i4 to'be made without disturbingthe gear ing connections.

In orderto'effectuat'e the driving oi" spindle by spindle sleeve gear 35y without interferinc with. the vertical movements of the spindle is produced by cam A,the spindle sleeve gear is'rig'i'dlysecured to the sleeve '55, which, as hrs been previously mentioned, is rotatably journalediuayertical recess 63d in the spindle support "frame 68. A key operates between sleeve 75 and a splined region the provided on the spindle 16. Hence, thespindle will be driven corotatively with spindle sleeve gear as and yet the vertical position of spindle l8 may be adiustedindependently of the rotational. movement imparted thereto.

From the foregoing description, it is clear that this invention provides convenient and ecoeffecting all of the four relative movements of the workpiece and cutting tool required in the practice of the vane generation methods dis closed by this invention. It should be particularly'notedthat each of the four relative movemerit components is produced independently of the other movements, yet timed relation therewith and may be'readiiy adjusted to con form to any-desired condition by suitable design of the'controllin'c cams A, B and C.

Referring to Figure 19. there is shown schematically the hydraulic circuit employed in connection with the described machine. The oil pump, whichm'av bathe pump 14, has its inlet connected through a suitable filter to a reservoir tank'Sfl. The outlet of the oil pump i connected through an a'diustablerelief valve 9| to the reservoir tank for the purpose of limiting the maximum pressuredeveloped by the pump. The antibacklash cylinder units 25 and 32 are connected in parallel to the outlet side of the pump and their bleed connections are connected to the reservoir tank. In addition, a return conduit is provided from each of the cylinder units through a shut-off valve 92 to the reservoir tank 90 for the purpose of relieving pressure on the pistons of the anti-backlash cylinder units without requiring that the pump be stopped.

Of course, if desired, a separate motor may be provided for driving the hydraulic pump and, as is generally the practice in machine tools, it may be desirable to provide an additional motor and pump (not shown) for circulating coolant over the workpiece and the cutting tool during the cutting operation.

In the modification of this invention illustrated in Figure 20, all of the machine elements heretofore described are utilized with the exception that a workpiece supporting fixture 5 i is employed which is suitably shaped so as to support a workpiece blank W for fabricating a single vane ele ment by the cutting action of the rotating tool. T. Obviously, when generating a single vane surface, it is not necessary to employ the indexing mechanism. for eifecting relative angular indexing of the work supporting spindle It with respect to the spindle sleeve 39.

In the modification of Figure 20, the work supporting fixture 5! is provided with an annular to the flange i3?) of the spindle it by the adjustable clamping ring 52. An angle fixture so is rigidly secured as by suitable bolts to an integral protuberance 5 i '13 formed on the work sup porting fixture 5!. The upstanding arm 811a of the angle fixture is provided with a thread-type chuck 8! for rigidly supporting cutter blade blank W by the threaded stem portion (not shown) of such blank, which is generally formed prior to the vane generation operation. the impeller vane blank W during the cutting operation, a support block 82 i rigidly secured to the base portion of angle fixture 80 beneath the blade blank V The top face of the support block 32 is contoured to exactly conform to that of the bottom face of the blade blank W so that the blade blank W is supported at all points. In particular, when cutting the second face of the blade blank W, then the top face of the supporting block will be contoured to correspond to the blade face which has been previously generated. Such support of the impeller blade blank during the vane generating cutting operation is found to be of tremendous value in insuring the dimensional accuracy of the resulting vane surface.

It should be particularly noted that in both modifications of the invention, the direction of movement of the cutter with respect to the workpiece is such as to produce a climb milling operation.

While any form of electrical control circuit for energizing the various driving motors of the machine may be employed, including a mere manual control arrangement, it is preferred to utilize a control circuit of the type set forth in Figure 18 wherein the various motors of the machine are successively energized in proper se quence to effect the rapid traverse of the workpiece toward the cutting tool prior to initiation of the cutting operation, the proper coordinated movements of the workpiece and cutting tool at proper speeds for a precision milling operation until the vane surface has been completely generated, and then the. reversal of relative movement between the workpiece and cutting tool to To rigidly support conical flange 5l'a by which it is rigidly secured tively provided in spaced relationship on the bed frame I0 adjacent to the path of movement of the movable first carriage [2 (Figures 3, 13-15). Actuating dogs for each of the limit switches, respectively DI, D2 and D3, are secured to an angle plate H12 in turn secured to movable carriage I 2 and respectively contact the limit switches LSI, LS2 and LS3 as the carriage i2 moves back and forth along the bed frame it). The location of the trip dogs with respect to the limit switches is, of course, selected so as to produce a control action at the proper time with respect to the relative position of the spindles l3 and it. Thus, switch L8! is normally closed and is held open only when the carriage I2 is in its retracted position. Switch LS3 is normally open but is momentarily closed by the movement of the carriage toward the milling position and effects the change in speed of the carriage from a rapid traverse to a feeding speed suitable for the milling operation. Switch LS2 is normally closed but is opened by the arrival of the carriag at the extreme forward position when the milling operation has been completed. Switch LS2 effects the reversal and return of the carriage to its starting position.

In Figure 18, there is shown in detail a preferred form of control circuit for effecting the proper energization of various motors of the apparatus heretofore described to produce the sequence of movements set forth above which are required in the machining of a single vane surface upon a workpiece. As is clearly shown in Figure 18, each of the various motors of the apparatus, i. e., the tool spindle driving motor 38, the vane generating movement driving motor 2e, and, if desired, a coolant motor 85 and a hydraulic pump motor 86 may be connected by various contactors to a three phase electrical power system Ll, L2 and L3. Thus, the spindle motor 34 has its terminals lTi, lTZ and iT3, respectively, connected to the power lines in either forward or reverse driving relationship by the contacts SF'a of relay SF or SRcz of relay SR.

The coolant motor 85 has its three terminal conductors ZTI, 2T2 and 2T3 connected to the three phase power line through the contacts of contactor C. The hydraulic pump motor 815 has its three phase line terminal 3T1, 3T2 re spectively, connected to the three phase line by the contacts of contactor H. The vane gener ating movement motor at is preferably of the two speed, reversible type and hence has a low speed winding (with terminals Ti, T2 and T3), cons nectable to the three phase line through the contacts FIa of contactor Ft. The terminals Ti 5, TL? and T13 of the high speed winding of motor 2d are respectively connected in either forward or reverse relationship with respect to the line terminals by the contacts RIa of contactor RI and contacts ROd of contactor R0.

The energizing coils for the various contaotors heretofore mentioned are controlled in proper sequence, as determined by the limit switches LSi, LS2 and LS3, by virtue of the connections set forth indetail in Figure 18. Several addianswer l tional switches :are. employed in the circuit of. Figure .18. Thus, an Git-0n .switchfii 31310- wlded for the enerciting of the-hydraulic pump Another swilch '95 controls .the .energization of the coolant motor t5. Lastly, a .main Stop switch 53% will tie-energize all parts of the machine. The entire control circuit operates. froma low voltaqn source such as the transformer Bl.

The various overload-cut-out switches, designated OIla-re connected directly in. series with the sec.- ondary of transformer .Si.

The operation of .the control circuit proceeds follows:

Switch is first-manually shifted to its closed position to effect the energization of contactor 1-1 and, by the closure of contactsH-a of contactor H, to energize the hydraulic pumprnotor 86. An additional. contact H--b is also closed whose function will appear later.

The cycle selector switch is then manually shifted to its'closed position, which position corresponds to the production of automatic opera tion of the machine, and an energizing circuit is thereby established for 'oontactor CR2 through the normally closed contacts of the stop switch '58 and the closed contacts H-o of contactor H. In addition, the contactor is energizcd'hy the closure of the contacts l-I-o of contactor'fi through an energizing circuit including the nornially closed contacts of limit switch In this condition, the depression. of the start cycle switch 89 will close an energizing circuit for contact-or RI, which may be traced through the normally closed contacts of limit switch LS2, the normally closed contacts PUG-c of a contactor R0, the normally closed contacts 93a of return switch t3, the closed contacts 89a of start cycle switch the normally closed con tacts GEL-Jo of contactor CR1, and the normally closed contacts FL-c of a contactor F1. ene gization of contactor RI effects the energization of the vane generating movement motor (it in a forward direction at a high speed.

by the closure of the contacts RL-a. Also, the contactor efiects a self-locking circuit around the contacts of start cycle switch 89 by virtue of the closing of contacts RI--b thereof. Hence, the release of start cycle switch 23% does not eiiect the de-energisation of contaetorRI.

As soon as the carriage l2 moves forward by the drive imparted by the vane generating movement motor 2%, the limit switch LS! is returned from its open position, in which it is heldat the extreme retracted position of the carriage, and permitted to close. The spindle motor at may then he energized in either direction by selectively manually moving the spindle motor control switch at. The coolant motor 85 may be energized by manually shifting the coolant motor switch 95 to its closed position. The energization of such motors is effectively accomplished by contactor SF or SE, in the case of the spindle motor, depending upon the desired direction of rotation of the spindle, and contactor-C in the case-of thecoolant motor. The-energizing circuits ior .contactors' LSF Q01- SR and contact r. bie'traced through thecl'osed contacts :of limit switch LS1, the closed contacts RE -d of contactor RI; and the appropriate set of closedcontactsof.spindlenrotor switches and the closed contacts :oicoolant motor switch 95. The 'energization of either contactor SF or SR, produces a locking. circuitaround contacts RI-d hy the respective closing of contacts SF-b or as the: oasemay'be;

When-the-carriage 1 2! moves forwardly to a position. justprior to the engagement of the rotating' cutting tool T with the workpiece W, the limit switch LS3 is actuatedzto close its contacts. Such momentary actuation of limit switch LS3 provides an energizing circuit for contactor CR! which may-betraced through the closed contacts oflimitswitch LS2, the-.normally closed contacts RO- eoi a contactor R0, the normally closed contacts 9.3a'oi returnswitch $3, the closed cont is GEL- a .of contactor CR2, the closed contactsnieontactor RI, and the closed contacts. oi switch. LS Relay CB1! efiectse selfloclting. clrcuitior itself by closure of its contacts GEM-1L arranged in parallel relationship to the contacts of shunt-switch LS3. -ence, thereuponing of limit switch LS3 produced. by further forward movement of the carriage- 42 has no effect upon the .energization of contactor CRi.

Energizationof contactor CR1 effects the openingofzits normally closed contacts Chit-73 which tie-energizes the contactor RI, and, hence, deenergizes the winding TH, TM, and Fri-.3 of the vane generating movement motor 26. Concurrently, the contactor FIis energized-by the closure ofcontacts CRL-c through acircuit which may he traced from-thenorrnallyclosed contacts 93a of return switch 93-, through the closed contacts GEE-wot contaetor CR2 the closed: contacts CR i--c of contactor CR1. Energization of con.- tactor F1 effects theenere'ization of the winding Ti, T2 and T3- of the vane'generating movement motor 28 to drive the motor inthesame-direction eutat areduced speed through the closure of contacts FI-oof .contactor Fl. Closure of contacts li'L-b-of contactorFI'effiects a locking circuit for the contaotor around the contacts CR!-c. Also,.normally closed contacts FI-c of contactor FIareopened to further insure the de-en'ergization of cont-actor RI. Likewise, normally closed contacts I'll-e ofcontactcr Flare-opened to insure the-de-energizationofoontactor RO. These will he recognized merely as conventional interlocking arrangements to insure that only one winding of the'vanejgenerating movement motor 26 isproperly energizedatany one time.

Lastly, normally opencontacts FI-d of contactor F1 are closed-to maintain the energization of contactnrsv SF or. SRxand contactor C independent of the opening of contact RId of contactor RI.

The vane; generating movement motor 21?, thereiore, operates at a proper speed for the milling operation and advances the carriage and, hence, the workpiece Wand cuttingtool T through the various V coordinated relative movements required to produce-a desired-vane surface upon the workpiece.

the-conclusion oi'then'iilling operation, the carriage -l-2 advances to a point where the limit SWltGh-L-SZlS actuatedtoopen its contacts. The actuation-of limit switch-LS2 has'the effect of immediatelyde-energizing contactors CR3, CRi, Fl, c i-of coursa naintaining contactor RIin a deenergizedcondition. :Hence-,'motor Zllis de-ener 

